Swash-plate hydraulic pressure device

Abstract: A swash-plate hydraulic pressure device for use as a hydraulic pump or motor includes a cylinder block having an annular array of cylinder holes defined therein around an axis. A plurality of plungers of a ceramic material are reciprocally movably disposed in the cylinder holes, respectively, the plungers having respective partly spherical tip ends. A swash plate of metal is disposed around the cylinder block for rotation with respect to the cylinder block, the swash plate having a dimple of a partly spherical cross section defined therein, the partly spherical tip ends of the plungers engaging in the dimple. The plungers have a pore area percentage of at most 7.8 % and a maximum surface roughness of at most 1.6 s. The partly spherical tip end of each of the plungers has a radius R₀ of curvature, each of the plungers has a diameter D, the dimple has a radius R₁ of curvature and a depth E. The ratios R₀/D, R₀/R₁, and E/R₀ are in the ranges of 0.52 ≦ R₀/D ≦ 0.62, 0.81 ≦ R₀/R₁ ≦ 0.87, and 0.36 ≦ E/R₀ ≦ 0.42. Each of the plungers has a beveled surface on an end thereof opposite to the partly spherical tip end thereof, the beveled surface having a depth of at least 0.6 mm.

Description: The present invention relates to a swash-plate hydraulic draulic pressure device such as a hydraulic pump or a draulic motor, and more particularly to a swash-plate pressure device having improved plungers and swash plate. One known swash-plate hydraulic pressure device is disclosed in Japanese patent application No. 3-199621, for example. The swash-plate hydraulic pressure device, which may be used as a hydraulic pump or a hydraulic motor includes a cylinder block having an annular array of cylinder holes defined therein around an axis and held in communication with an oil passage, and a plurality of plungers reciprocally movably disposed in the cylinder holes, respectively. A swash plate rotatable relatively to the cylinder block is disposed in surrounding relation to the cylinder block. The swash plate has an annular array of partly spherical recesses defined therein and held in abutment against respective partly spherical tip ends of the plungers. When the swash plate is rotated with respect to the cylinder block, the plungers are caused to move reciprocally in the respective cylinder holes for drawing and discharging working oil into and out of the cylinder holes. At this time, the swash-plate hydraulic pressure device operates as a hydraulic pump. Alternatively, working oil is introduced into and discharged out of the cylinder holes to move the plungers reciprocally in the respective cylinder holes, forcing the swash plate to rotate with respect to the cylinder block. At this time, the swash-plate hydraulic pressure device operates as a hydraulic motor. Heretofore, both the plungers and the swash plate are made of steel. Under rigorous operating conditions, e.g., when the swash-plate hydraulic pressure device rotates at a high speed or under a high hydraulic pressure, however, the steel plungers tend to wear rapidly. US-A-4 741 251 describes a swash-plate hydraulic pressure device according to the preamble of claim 1. Japanese laid-open patent publication No. 62-104616 discloses a guide roller for rolling a wire rod of metal. The disclosed guide roller is made of a ceramic material which is highly resistant to wear and heat, and highly lubricatable. Specifically, the disclosed guide roller is made of silicon nitride havinq a porosity of 1 % or less and a surface roughness of 6 µm (s) or lower. However, the disclosed ceramic material cannot directly apply to the plungers of the swash-plate hydraulic pressure devices. Specifically, since the plungers are subject to a much higher pressure than the disclosed guide roller, if the maximum surface roughness (Rmax) of the plungers were 6µm(s) then an oil film would be broken between the tip ends of the plungers and the swash plate, resulting in a direct contact between the plungers and the swash plate and hence a localized increase in the pressure between the plungers and the swash plate. The porosity of a ceramic material, which is the ratio of the volume of pores of the material to the volume of the material, is not necessarily an exact representation of conditions of contacting surfaces of the plungers and the swash plate. Another problem is that because the elastic coefficient and coefficient of friction of the ceramic materials are different from those of the steel, ceramic plungers would suffer abnormal wear and seizure and be liable to jump out of the recesses of the swash plate in high-speed and high-pressure operation if the ceramic plungers were of the same dimensions and shape as the steel plungers. It is therefore an object of the present invention to provide a swash-plate hydraulic pressure device which has plungers of a ceramic material that are effective to reduce wear on or damage to a swash plate, highly resistant to wear and scoring, and are prevented from jumping out of a dimple defined in the swash plate. According to the present invention, there is provided a swash-plate hydraulic pressure device comprising a cylinder block having an annular array of cylinder holes defined therein around an axis and suction and discharge oil passages defined therein, valve means for selectively bringing the suction and discharge oil passages into communication with the cylinder holes, a plurality of plungers reciprocally movably disposed in the cylinder holes, respectively, the plungers having respective tip ends, and a swash plate disposed around the cylinder block for rotation with respect to the cylinder block, the tip ends of the plungers being held against the swash plate, the swash plate being made of metal; unlike in US-A-4 741 251, the plungers are made of a silicon nitride and have a pore area percentage of at most 7.8% and a maximum surface roughness of at most 1.6µm (s). Preferably, the pore area percentage is of at most 3.21 %, and the maximum surface roughness is of at most 1.2 µm (s). According to the present invention, the plungers may have respective partly spherical tip ends, and the swash plate of metal disposed around the cylinder block for rotation with respect to the cylinder block may have a dimple of a partly spherical cross section dfined therein, the partly spherical tip ends of the plungers engaging in the dimple; if the partly spherical tip end of each of the plungers having a radius R 0 of curvature, and each of the plungers having a diameter D, the ratio of the radius R 0 of curvature to the diameter D may be in the range of 0.52 ≤ R 0 /D ≤ 0.62. Preferably, the ratio is in the range of 0.55 ≤ R 0 /D ≤ 0.60. Now, if the dimple has a radius R 1 of curvature, the ratio of the radius R 0 of curvature to the radius R 1 of curvature may be in the range of 0.81≤R 0 /R 1 ≤0.87. Now, if the dimple has a depth E, the ratio of the radius R 0 of curvature to the depth E being in the range of 0.36≤E/R 0 ≤0.42. The above and other objects, features and advantages of the present invention will become apparent from the following description when taken in conjunction with the accompanying drawings which illustrate preferred embodiments of the present invention by way of example. FIG. 1 is a cross-sectional view of a swash-plate hydraulic pressure device according to the present invention, the swash-plate hydraulic pressure device being used as a hydraulic pump in a hydrostatic continuously variable transmission on a motorcycle; FIG. 2 is an enlarged fragmentary cross-sectional view showing a region in which a plunger and a swash plate contact each other; FIG. 3 is an enlarged fragmentary cross-sectional view of the region shown in FIG. 2; FIG. 4 is a graph showing certain ranges of surface roughnesses and pore area percentages of plungers; FIG. 5 is an enlarged fragmentary cross-sectional view showing another region in which a plunger and a swash plate contact each other; FIG. 6 is a graph showing the relationship between a ratio R 0 /D, a hydraulic pressure, dimple damage, and plunger jumping; FIG. 7 is a graph showing the relationship between a ratio R 0 /R 1 , the hydraulic pressure, abnormal wear, and the plunger jumping; FIG. 8 is a graph showing the relationship between a ratio L/R 0 , the hydraulic pressure, the abnormal wear, and the plunger jumping; As shown in FIG. 1, a swash-plate hydraulic pressure device according to the present invention is used as a hydraulic pump in a hydrostatic continuously variable transmission on a motorcycle, for example. The swash-plate hydraulic pressure device comprises a cylinder block 1 having an annular array of cylinder holes 2 defined therein at equal angular intervals around an axis L, and a plurality of plungers 3 reciprocally movably disposed in the cylinder holes 2, respectively. The plungers 3 are made of a ceramic material composed primarily of silicon nitride (Si 3 N 4 ) or the like. The cylinder block 1 has a hollow shaft 4 extending away from the cylinder holes 2 coaxially with the axis L. The swash-plate hydraulic pressure device also includes a hollow rotor 6 rotatably supported on the cylinder block 1 and the shaft 4 by bearings 5. The rotor 6 has a sprocket 7 disposed on an axially intermediate outer circumferential surface thereof. A chain 8 is trained around the sprocket 7 and the crankshaft (not shown) of the engine of the motorcycle. The rotor 6 has an eccentric ring end portion 9 disposed around the cylinder holes 2 in eccentric relation to the axis L. A swash plate 10 is rotatably supported on an axially intermediate inner circumferential surface of the rotor 6 by a thrust bearing 11 and a radial bearing 12. The swash plate 10 is made of steel (SUJ2 HRC60 - 65) having a surface roughness of 3.2µm (s). The swash plate 10 is disposed around the shaft 4 and has its plane tilted with respect to the axis L. The swash plate 10 has an annular recess or dimple 13 of a partly spherical cross section defined in an axial surface thereof and held in abutment against partly spherical tip ends of the plungers 3. In the case when operating conditions are not so rigorous,the dimple 13 is not always necessary and a swash plate 10 has a flat surface against spherical tip ends of the plungers. The cylinder holes 2 define respective oil chambers therein which are held in selective communication with a discharge oil passage 15 or a suction oil passage 16 defined in the cylinder block 1 through valves 14. The valves 14 are normally urged radially outwardly by springs (not shown), and have respective radially outer ends held against a bearing 17 which is in turn held against an inner circumferential surface of the eccentric ring end portion 9. When the engine operates the rotor 6 is rotated about the axis L, rotating the swash plate 10 around the shaft 4. As the swash plate 10 rotates, those of the plungers 3 which are in a discharge region, i.e., the upper plungers 3 in FIG. 1, are moved to the left, compressing the oil chambers. At this time, the valves 14 associated with the plungers 3 in the discharge region are pushed downwardly by the eccentric ring end portion 9. The oil chambers in the cylinder holes 2 which accommodate the plungers 3 in the discharge region are now brought into communication with the discharge oil passage 15, allowing oil to be discharged from the oil chambers into the discharge oil passage 15. The valves 14 associated with the plungers 3 in the suction region are pulled downwardly by the eccentric ring end portion 9. The oil chambers in the cylinder holes 2 which accommodate the plungers 3 in the suction region are now brought into communication with the suction oil passage 16, allowing oil to be drawn from the suction oil passage 16 into the oil chambers. The introduced oil displaces those of the plungers 3 which are in the suction region, i.e., the lower plungers 3 in FIG. 1, to the right while being held in contact with the swash plate 10. The hydrostatic continuously variable transmission includes another swash-plate hydraulic pressure device (not shown) in the form of a hydraulic motor which can be actuated by the hydraulic pump shown in FIG. 1. The hydraulic motor is mounted in a leftward extension of the rotor 6, and comprises an annular array of plungers reciprocally disposed in respective cylinder holes defined in a leftward extension of the cylinder block 1, and a variable-angle swash plate rotatably supported in the leftward extension of the rotor 6. Oil chambers defined in the cylinder holes of the hydraulic motor are held in communication with the oil chambers defined in the cylinder holes 2 of the hydraulic pump through the discharge oil passage 15 and the suction oil passage 16. The oil discharged from the hydraulic pump through the discharge oil passage 15 flows into the cylinder holes of the hydraulic motor, projecting those plungers which are in an expansion region. The projected plungers rotate the swash plate of the hydraulic motor. As the swash plate of the hydraulic motor rotates, those plungers of the hydraulic motor which are in a contraction region are retracted, forcing oil to flow out of the corresponding cylinder holes through the suction oil passage 16 into the cylinder holes 2 which accommodate the plungers 3 in the suction region. The cylinder block 1 is now rotated under the sum of a reactive torque received from the swash plate 10 of the hydraulic pump and a reactive torque received from the swash plate of the hydraulic motor. When the angle of the swash plate of the hydraulic motor is varied, the reactive torque received from the swash plate of the hydraulic motor is varied for thereby varying the rotational speed of the cylinder block 1. Therefore, the hydrostatic continuously variable transmission can continuously vary the speed reduction ratio. As shown in FIG. 2, the partly spherical tip end of each of the plungers 3, which are made of a ceramic material composed primarily of silicon nitride (Si 3 N 4 ) or the like, has a number of pores 18 in its surface contacting the surface of the dimple 13, and an oil film 19 is interposed between the surface of the partly spherical tip of the plunger 3 and the surface of the dimple 13. The pores 18 in the surface of the partly spherical tip of the plunger 3 which contacts the surface of the dimple 13 have a pore area percentage of 7.8 % or less, preferably 3,21 % or less. As shown in FIG. 3, the surface of the partly spherical tip of the plunger 3 which contacts the surface of the dimple 13 has a maximum surface roughness (Rmax) of 1.6 µm (s) or less, preferably 1.2 µm (s) or less. If the pore area percentage exceeded 7.8 % and the maximum surface roughness (Rmax) exceeded 1.6 µm (s), then the surface of the dimple 13 in the swash plate 10 would wear too rapidly, as can be seen from FIG. 4. Each of the pores 18 should have a size of 50 µ or less because larger pores would reduce the mechanical strength of the plungers 3. FIG. 4 shows showing certain ranges of surface roughnesses and pore area percentages of plungers. The data in the graph shown in FIG. 4 were obtained from a durability test of plungers in which the swash-plate hydraulic pressure devices was rotated at 3,600 rpm under a hydraulic pressure of 450 kg/cm 2 for 20 hours. In the durability test, the plungers were subjected to a pressure of 200 kg/mm 2 and a peripheral speed of 0.01 m/s. In FIG. 4, those marked with O indicate plungers which cleared the durability test, those marked with Δ indicate plungers which cleared the durability test, but exhibited wear, and those marked with X indicate plungers which did not clear the durability test. As shown in FIG. 5, the partly spherical tip end, denoted at 3a, of each of the plungers 3 which is reciprocally movably disposed in the corresponding cylinder hole 2 is held against the surface of the dimple 13. The plunger 3 has a diameter of D, and the plunger tip end 3a has a radius R 0 of curvature. The surface of the dimple 13 has a radius R 1 of curvature and a depth E. FIG. 6 shows the relationship between a ratio R 0 /D, a hydraulic pressure acting on the plunger 3, damage to the dimple 13, and jumping of the plunger 3 out of the dimple 13 when the plunger 3 rotates with respect to the swash plate 10 at 3,600 rpm. As can be seen from FIG. 6, if the ratio R 0 /D were smaller than 0.52, then the dimple 13 would be cracked or otherwise damaged . This is because if the ratio R 0 /D were smaller than 0.52, then the plunger 3 would contact the dimple 13 under an increased pressure, and the introduction of oil between the partly spherical tip end 3a and the dimple 13 would become intermittent, causing the partly spherical tip end 3a to wear the dimple 13. If the ratio R 0 /D were greater than 0.62, then the partly spherical tip end 3a would tend to jump out of the dimple 13. This is because if the ratio R 0 /D were greater than 0.62, the point of contact between the partly spherical tip end 3a and the dimple 13 would be shifted radially outwardly. Therefore, the ratio R 0 /D should be in the range of 0.52 ≤ R 0 /D ≤ 0.62, and preferably in the range of 0.55 ≤ R 0 /D ≤ 0.60. FIG. 7 shows the relationship between a ratio R 0 /R 1 , the hydraulic pressure acting on the plunger 3, abnormal wear on the plunger 3, and jumping of the plunger 3 out of the dimple 13 when the plunger 3 rotates with respect to the swash plate 10 at 3,600 rpm. It can be seen from FIG. 7 that if the ratio R 0 /R 1 were smaller than 0.81, then the plunger 3 would suffer abnormal wear and scoring, and it the ratio R 0 /R 1 were greater than 0.87, then the partly spherical tip end 3a of the plunger 3 would jump out of the dimple 13, for the reasons described above. Therefore, the ratio R 0 /R 1 should be in the range of 0.81 ≤ R 0 /R 1 ≤ 0.87. FIG. 8 shows the relationship between a ratio E/R 0 , the hydraulic pressure acting on the plunger 3, abnormal wear on the plunger 3, and jumping of the plunger 3 out of the dimple 13 when the plunger 3 rotates with respect to the swash plate 10 at 3,600 rpm. The graph shown in FIG. 8 indicates that if the ratio E/R 0 were smaller than 0.36, then the partly spherical tip end 3a of the plunger 3 would jump out of the dimple 13, and if the ratio E/R 0 were greater than 0.42, then the plunger 3 would suffer abnormal wear and scoring. Therefore, the ratio E/R 0 should be in the range of 0.36 ≤ E/R 0 ≤ 0.42. Although certain preferred embodiments of the present invention has been shown and described in detail, it should be understood that various changes and modifications may be made therein without departing from the scope of the appended claims.

Claims: A swash-plate hydraulic pressure device comprising : a cylinder block (1) having an annular array of cylinder holes (2) defined therein around an axis (L) and suction (16) and discharge (15) oil passages defined therein ; valve means (14) for selectively bringing said suction and discharge oil passages into communication with said cylinder holes ; a plurality of plungers (3) reciprocally movably disposed in said cylinder holes, respectively, said plungers having respective tip ends ; and a swash plate (10) disposed around said cylinder block for rotation with respect to the cylinder block, said tip ends of the plungers being held against said swash plate ; said swash plate (10) being made of metal, characterized in that said plungers (3) are made of silicon nitride and have a pore area percentage of at most 7.8% and a maximum surface roughness of at most 1.6 µm. A swash-plate hydraulic pressure device according to claim 1, wherein said pore area percentage is of at most 3.21%, and said maximum surface roughness is of at most 1.2 µm. A swash-plate hydraulic pressure device according to claim 1, wherein said plungers (3) have respective partly spherical tip ends, and said swash plate (10) has a dimple (13) of a partly spherical cross section defined therein, said partly spherical tip ends of the plungers engaging in said dimple. A swash-plate hydraulic pressure device according to claim 3, wherein said partly spherical tip end of each of said plungers has a radius R 0 of curvature, and each of said plungers (3) has a diameter D, the ratio of the radius R 0 of curvature to the diameter D being in the range of 0.52≤R 0 /D≤0.62. A swash-plate hydraulic pressure device according to claim 4, wherein said ratio is in the range of 0.55≤R 0 /D≤0.60. A swash-plate hydraulic pressure device according to claim 3, wherein said partly spherical tip end of each of said plungers has a radius R 0 of curvature, and said dimple has a radius R 1 of curvature, the ratio of the radius R 0 of curvature to the radius R 1 of curvature being in the range of 0.81≤R 0 /R 1 ≤0.87. A swash-plate hydraulic pressure device according to claim 3, wherein said partly spherical tip end of each of said plungers has a radius R 0 of curvature, and said dimple has a depth E, the ratio of the radius R 0 of curvature to the depth E being in the range of 0.36≤E/R 0 ≤0.42.

Inventors: HAYASHI TSUTOMU, IWATOMO JUN, KAMIDE NAOKI, KAWAKAMI YASUNOBU, OHTA NAOKI, HAYASHI, TSUTOMU, IWATOMO, JUN, KAMIDE, NAOKI, KAWAKAMI, YASUNOBU, OHTA, NAOKI, HAYASHI, TSUTOMU, C/O K.K. HONDA GIJUTSU KENKYUJO, IWATOMO, JUN, C/O K.K. HONDA GIJUTSU KENKYUJO, KAMIDE, NAOKI, C/O K.K. HONDA GIJUTSU KENKYUJO, KAWAKAMI, YASUNOBU, C/O KK HONDA GIJUTSU KENKYUJO, OHTA, NAOKI, C/O K.K. HONDA GIJUTSU KENKYUJO
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1994
Main classification: F04B1
IPC codes: F04B1